Adjustable diameter roller bearing

ABSTRACT

An adjustable diameter roller bearing is mounted upon an internal stationary member having an axis of rotation. An external rotor is disposed to rotate about the axis of rotation. In order to reduce the cost of manufacturing the mating parts while holding to the required tolerances, the subject bearing has an adjustable diameter or is radially shiftable. A support means having at least one axially movable ring is carried on the stationary member. A split raceway is mounted upon the support means to be radially shiftable responsive to axial movement of the ring. A roller cage having a plurality of circumferentially spaced rollers is rotatively disposed upon the raceway means. Adjustable positioning means are connected to the support means to axially shift the support means and the raceway to force the rollers concentrically to engage the rotor. The support means are concentric to the axis of rotation, and by engaging the raceway, cause the raceway also to be concentric. Adjusting the diameter of the roller bearing causes the rotor to be likewise centered with respect to the axis of rotation. Wedge means in the form of annular chamfers or arcuate shoulders, are used to expand or contract the diameter of the raceway, while annular garter springs urge the raceway to contact the support means.

States Patent llrrite Schneider [54] ADJUSTABLE DIAMETER ROLLER [52] US.Cl. ..308/l96 [51] Int. Cl. ..Fl6c 33/30 [58] Field of Search ..308/l96,189, 207, 208

[56] References Cited UNITED STATES PATENTS 1,195,952 8/1916 Fox..308/l96 Primary Examiner-Charles J. Myhre Assistant ExaminerFrankSusko Anorney Marshall J. Breen et al.

[57] ABSTRACT An adjustable diameter roller bearing is mounted upon aninternal stationary member having an axis of 1Marcli 20, 1973 rotation.An external rotor is disposed to rotate about the axis of rotation. Inorder to reduce the cost of manufacturing the mating parts while holdingto the required tolerances, the subject bearing has an adjustablediameter or is radially shiftable. A support means having at least oneaxially movable ring is carried on the stationary member. A splitraceway is mounted upon the support means to be radially shiftableresponsive to axial movement of the ring. A roller cage having aplurality of circumferentially spaced rollers is rotatively disposedupon the raceway means.

Adjustable positioning means are connected to the support means toaxially shift the support means and the raceway to force the rollersconcentrically to engage the rotor. The support means are concentric tothe axis of rotation, and by engaging the raceway, cause the racewayalso to be concentric. Adjusting the diameter of the roller bearingcauses the rotor to be likewise centered with respect to the axis ofrotation. Wedge means in the form of annular chamfers or arcuateshoulders, are used to expand or contract the diameter of the raceway,while annular garter springs urge the raceway to contact the supportmeans.

24 Claims, 18 Drawing Figures ADJUSTABLE DIAMETER ROLLER BEARINGBACKGROUND OF THE INVENTION SUMMARY OF THE INVENTION It is therefore anobject of the present invention to provide an improved adjustablediameter roller hearing which overcomes the prior art disadvantages;which is simple, economical and reliable; which uses an axially movablesupport means; which has a split raceway; which maintains concentricityof the rotating parts with an axis of rotation; which has wedge meanscapable of expanding or contracting the raceway; which uses one or morespaced rings; and, which has positioning means that clamp the racewaybetween the support members, thus forcing the raceway into a concentricposition with respect to the axis of rotation.

Other objects and advantages will be apparent from the followingdescription of several embodiments of the invention, and the novelfeatures will be particularly pointed out hereinafter in the claims.

BRIEF DESCRIPTION OF THE DRAWINGS This invention is illustrated in theaccompanying drawings in which:

FIG. 1 is a sectional side elevation showing a preferred embodiment ofthe invention.

FIG. 2 is a sectional, front elevational view taken substantially alonglines 2-2, as shown in FIG. 1.

FIG. 3 is a greatly enlarged, broken away side elevational view of thenovel bearing of the present inventron.

FIG. 4 is an exploded perspective view of the improved bearing of thepresent invention.

' FIG. 5 is a greatly enlarged view, broken away, of the improvedbearing of the present invention showing a diagrammatic representationof the axial and radial shifting of the raceway thereof.

FIG. 6 is a rear elevational view, partly broken away, of the improvedbearing of the present invention.

FIG. 7 is a top plan view, partly in section, of the rotary meansincluding the cage means and rollers.

FIG. 8 is a partial, sectional, side elevation showing another preferredembodiment of the present inventron.

FIG. 9 is a greatly enlarged, broken away view, showing the improvedbearing of FIG. 8.

FIG. 10 is an exploded perspective, partly in section, of the improvedbearing of FIG. 8.

FIG. 11 is a top plan view, in section, ofa portion of the roller cageand rollers.

FIG. 12 is a partial top plan view of the split raceway and springsmounted thereon.

FIG. 13 is an enlarged, broken away, and sectional side elevational viewof the improved bearing, showing the bearing in unadjusted,non-concentric position.

FIG. 14 is a broken away, sectional, side elevational view of theimproved bearing in adjusted, assemble concentric position.

FIG. 15 is a greatly enlarged partial, sectional, side elevational viewof the wedge means corresponding to FIG. 13.

FIG. 16 is a partial, sectional, side elevational view of the wedgemeans corresponding to FIG. 14.

FIG. 17 is a view of the improved bearing corresponding to FIG. 13,showing a diagrammatic representation of the bearing in unadjusted,non-concentric position.

FIG. 18 is a view corresponding to FIG. 14, showing the improved bearingin adjusted, concentric position.

DESCRIPTION OF THE INVENTION In the embodiment of the inventionillustrated in FIGS. 1-7, the novel bearing assembly, designatedgenerally 20, is shown embodied in a positive displacement rotary meter22. The meter 22 is briefly described herein, but for a more detaileddescription thereof, reference may be had to U.S. Pat. No. 3,554,032,granted Jan. 12, 1971, and entitled Rotary Fluid Meter.

The meter 22, as shown in FIG. 1, has a stationary housing 24 with acentral opening 26. This opening 26 is closed at one end by the integralend member 28, and is closed at the other end by the bonnet 30 attachedto the housing 24 by fastenings 32. The housing 24 has an inlet passage34 and an outlet passage 36 illustrated in FIG. 2. A stationary liner 38is positioned within the bore 26 and is fixed to the housing 24 by meansof the fasteners 40. The housing 24 and the liner 38 are part of thestationary body 42. The liner 38 has an inlet opening or port 41 alignedwith the inlet passage 34, and an outlet opening or port 43, alignedwith the outlet passage 36, as depicted in FIG. 2. A gasket 44 isclamped between the housing 24 and the liner 38, in the region of theinlet an outlet ports 41 and 43, respectively. A stationarycrescent-shaped member 46 is provided with an end flange 48, fixed tothe liner 38 by fastenings 50. The member 46 has an outer wall surface52 shown in FIG. 1 which is concentric with the inner wall surface 54inthe liner 38, and these walls define an arcuate channel 56 between them.The arcuate channel 56 receives the blades 58 of a rotor 60 which ismounted to rotate within the liner 38. An offset cavity 62 within theliner 38 is defined by the concave cylindrical surfaces 64 and 66, andthis cavity 62 intercepts the arcuate channel 56. A rotary gate 68 ismounted to turn in the offset cavity 62 and its outer cylindricalsurface 70 fits closely within the surfaces 64 and 66. The surface 70 isinterrupted to provide entrance openings 72 into separate pockets 74 and76, formed within the rotary gate 68 as illustrated in FIGS. 1 and 2.The end walls 78 of the rotary gate 68 are cut away, as shown at 80, toprovide clearance for the rotor blades 58. The axis of rotation 82 ofthe rotor 60 intercepts the offset cavity 62 and the path of movement ofthe rotary gate 68 because the diameter of the rotary gate is greaterthan one-half the diameter of the rotor 60.

For convenience in assembly, the member 46 includes a stationary plate84 fixed thereto by fastenings 86. A front bearing assembly 88 ismounted in the plate 84 and supports a trunnion 90 fixed on the endflange 92 of the rotor 60. The rotor blades 58 are secured to this endflange 92 by means of threaded fastenings 94, and depicted in FIG. 1.

An end ring 96 illustrated in FIG. 1 is secured to the other end of therotor blades 58 by means of fastenings 98, and the end ring 96 isprovided with a circular trackway 100. The trackway 100 is contacted bya plurality of circumferentially spaced rollers 102 of the bearingassembly 20 as illustrated in FIGS. 1, 2 and 3, for purposes more fullydescribed hereinafter. Accordingly, one end of the rotor 60 is supportedby means of the trunnion 90 and bearing 88, and the other end issupported by means of the rollers 102 of the bearing assembly 20 and thetrackway 100.

The rotary gate 68 is supported on axially spaced bearings 104 and 106.The bearing 104 is carried on the plate 84 and the bearing 106 iscarried on the crescent-shaped member 46. The parallel end walls 78 onthe rotary gate 68 have running clearance with a stationary wall 108 andsurface 110 of the plate 84, respectively. An external spur gear 112 isfixed to the rotary gate 68 and meshes with the internal spur gear 114provided on the ring 96 of the rotor 60. The gear 112 is mounted withina clearance pocket 116 provided on the member 46. The fixed diameter ofthe gear 112 is one-half that of the internal gear 114, so that therotary gate 68 turns at twice the speed of the rotor 60. Thus, the twopockets 74 and 76 in the rotary gate 68 are adequate for successivereception of the four rotor blades 58.

A mechanism for driving a counter or other readout register device isconveniently mounted in the bonnet 30. In the register depicted in FIG.1, an axially projecting offset pin 118 on the rotor flange 92 engages aradially projecting arm 120, fixed to a shaft 122. A magnetic couplingdevice 124 connects the shaft 122 to a shaft 126. The shaft 126 drives ashaft 128 and a coupling 130 through a speed reducing gear train 132. Asuitable counter mechanism (not shown) is mounted on the bonnet flange134 and arranged to be driven by the coupling 130.

The trackway 100 and the internal gear 114 form a portion of the outerboundary of an annular space 136 into which the bearing assembly 20 andthe gear 112 project. The only openings through which fluid can flowinto the annular space 136 are the long labyrinth seals formed by therunning clearances between the rotating and stationary parts, since theback opening thereof is closed by means of a cover plate 138. Dirtparticles in the fluid stream are thus excluded from the bearings, gearsand trackway.

In operation, the housing flanges at the inlet 34 and outlet 36 areconnected to suitable piping (not shown). Fluid under pressure isadmitted through the inlet passage 34 and opening 41, and into theannular channel 56. Fluid pressure acting on the upstream side of one ofthe rotor veins 58 (shown at the 3 oclock position in FIG. 2), causesthe rotor 60 to turn within the liner 38 in a clockwise direction. Thegearing 112, 114 turns the rotary gate 68 in a clockwise direction attwice the speed. The rotary gate 68 prevents direct flow from the inlet34 to the outlet 36 and requires the fluid to flow through the annularchannel 56. Each of the rotor blades 58 is received in one of the gatepockets 74 or 76 as it passes from a position near the outlet 36 to aposition near the inlet 34. Rotation of the rotor 60 is transmittedthrough the pin 118 and the shaft 122, magnetic coupling 124, andthrough the gear train 132 to drive the coupling 130. The fluid exitsthe channel 56 through the port 43 and outlet passage 36 as shown inFIG. 2.

In part, because of the large diameter, it is more critical that themating parts hold to the required tolerances at the bearing assembly 20,and anywhere else in the meter 22. The embodiment of the presentinvention illustrated in FIGS. 1-7 is intended for use in retrofittingand otherwise conventional meter 22. A bushing 140 is disposed in anaperture 142 formed in the end flange 48, so as to adapt the existinghole diameter of aperture 142 to a screw 144 having an enlarged bodyportion 146, intermediate threaded ends 148, and respectively, with thediameter at end 148 slightly larger than that of the end 150 as viewedin FIG. 3.

The bearing assembly 20 as best seen in FIGS. 3 and 4, includes asupport means 152 having a floating ring 154 axially spaced from a splitsupport ring 156 and a back up ring 158, a split raceway or innerbearing race 160, upon which is rotatively mounted a rotary means 162having a cage means 164 and a plurality of circumferentially spacedcylindrical rollers 102, with the means 162 disposed in superposition toa pair of axially spaced garter springs 168 which act to radiallycollapse the raceway 160, and the screws 144, which act as positioningmeans as more fully explained hereinafter.

The raceway as seen in FIGS. 3 and 5, has an inner trackway 170 formedon its outer circumference intermediate a pair of axially spaced annulargrooves 172. The cylindrical rollers 102 will rotate about the trackway170, while the springs 168 are disposed in the annular grooves 172. Theinner circumference includes a straight intermediate section 174 whichlies substantially parallel to the bottom surface of the trackway 170.The opposite ends of the intermediate section 174 terminate in wedgemeans 176 which take the form of chamfered edges 178 which extendradially upwardly and outwardly in a direction away from each other. Theraceway 160 has an oblique or transverse split as at 180, which permitsadjustment of the diameter of the raceway 160 by means of expansion orcontraction thereof.

Inwardly of the end flange 48, the crescent-shaped member 46 has acircular section 182 which has arcuate recesses 184 radially inwardly ofthe three screws 144 which are uniformly circumferentially spaced at 120intervals. The axis of the circular section is coincident to the axis ofrotation 82, while the screws 144 are mounted in the end flange 48 atradially equal distance from the axis 82.

The floating ring 154 has an inner diameter slightly larger than thediameter of the circular section 182, and is formed substantially round.A plurality of holes 186 are formed in alignment with the screws 144. Anarcuate shoulder 188 is formed on the end of the floating ring 154adjacent the end flange 48 and extends from an intermediate point on theouter circumference thereof, to form an arcuate surface which extendsradially upwardly and outwardly in the direction of the end flange 48.The support ring 156 has a similar arcuate shoulder 190 formed thereon,but extending in the opposite direction away from the end flange 48. Thesupport ring 156 is circular, with a split at 192 and a plurality ofholes 194 formed in alignment with the screws 144. Each of the rings154, 156 has a flat annular section 196 which are axially spaced as at219 from each other and are disposed in face to face relationship. Thesections 196 have a smaller outer diameter than that of the highestpoint on the respective shoulders 188 and 190. The shoulders 188 and 190coact to define wedge means 198, formed for purposes more fullydescribed hereinafter. The annular back up ring 158 has an innerdiameter slightly larger than the diameter of the circular section 182.A plurality of tapped holes 200 are formed in the ring 158 in alignmentwith the screws 144. The end 150 of the screws 144 will pass through theholes 186 and 194 to be threadedly engaged in the tapped holes 200, soas to position the raceway 160 between the rings 154 and 156, as shownin FIGS. 3 and 5.

The cage means 164 illustrated in FIGS. 3, 4, 6 and 7, have a pair ofannular retaining rings 202, which are axially spaced by a spacer 204held in position by a screw 206 passing through holes 2080 and 208b, thelatter of which is tapped, so as to hold the cage means 164 in assembledposition. The roller 102 is mounted on the enlarged center portion 2100fa pin or axle 212 with the roller 102 free to rotate relative thereto.The roller 102 has integral spacers 214 formed at either end thereof, ofgreatly reduced diameter so as to prevent binding of the roller 102against the retainer rings 202. The connection between the rollers 102,the pins 212, and the retainer rings 202, is sufficiently loose topermit the designed amount of diameter adjustment of the raceway 160.The retainer rings 202 have a diameter sufficiently large so as topermit the rollers 102 to be seated within the inner trackway 170 of theraceway 160, while providing for the desired amount of expansion orcontraction of the raceway 160.

In the bearing assembly 20, as illustrated in FIG. 3, the retainer rings202 are disposed radially outwardly of the springs 168 which urge theraceway 160 to collapse into contact with the rings 154 and 156 of thesupport means 152.

The present embodiment of the invention can be used for retrofitting anotherwise conventional meter 22 with the novel bearing assembly 20. Inthis form, and because of manufacturing tolerances on both the bearingtrack on the circular section 182 of the member 46 and the trackway 100of the rotor 60, it is necessary to adjust both the outside diameter ofthe raceway 160 and the inside diameter of the support ring 156, each ofwhich are split, as at 180 and 192, respectively.

Since the support ring 156 is split at 192, the spring bias of theannular garter spring 168 acts through the raceway 160 to clamp thesupport ring 156 upon the threaded end 148 thereof, which extends beyondthe bushing and is fitted with a washer 216 and a nut 218. Rotation ofthe nut in one direction or the other will control the axial position ofthe back up ring 158 which also repositions the support ring 156, anddue to the wedging action of the arcuate shoulders 188 and 190,respectively, on the chamfered edge 178 at either side of the raceway160, the diameter of the raceway 160 will be either expanded orcontracted.

The initial mounting of the bearing assembly 20 will place the floatingring 154 in abutment with the end flange 48 and bushings 140, whichposition may be considered as axially fixed in that the floating ring154 will not shift or change axial position during adjustment of thebearing assembly 20. The opposite ends of the intermediate section 174terminate in wedge means 176 which take the form of chamfered edges 178which extend radially upwardly and outwardly in a direction away fromeach other.

The raceway 160 has an oblique or transverse split as at 180, whichpermits adjustment of the diameter of the raceway 160 by means ofexpansion or contraction thereof. In FIG. 5, the raceway 160 isillustrated as being supported upon the shoulders 188 and 190 in a firstposition in the full line representation wherein the support rings 154and 156 are axially spaced from each other by a certain distancedescribed generally by the reference character 219. The rotary means 162and the garter springs 168 are not shown in the diagrammaticrepresentation of FIG. 5. Assuming the diameter adjustment to be maderequires expansion of the raceway 160, upon adjustment by thepositioning means 201, made up of the screws 144 and nuts 218, thesupport ring 156 and the raceway 160 will assume an adjusted positionrepresented by the dotted lines of FIG. 5 wherein the support ring 156is shifted axially toward the ring 154 to lessen the space 219, whilethe raceway 160 is shifted both axially toward ring 154 and radiallyoutwardly therefrom. This is the same movement which the support ring156 and raceway 160 will partake in respective assembled position in thebearing assembly 20 when the diameter of the raceway 160 requiresexpansion.

In the other preferred embodiment of the invention illustrated in FIGS.8-18, the novel bearing assembly, designated generally 220, is shownembodied in a positive displacement rotary meter 22a. The meter 22a issubstantially the same as meter 22, and for the most part, like partsand components will have similar reference characters for bothembodiments of the present invention, except, mainly as relates to thebearing assembly 220, wherein certain components will use theircounterparts reference character having a suffix a, while othercomponents, again mainly related to the bearing assembly 220 will bereferred to by a new reference character.

Accordingly, the meter 22a has a stationary housing 24 having an inletand outlet passage (not shown) for fluid to flow into the meter 22a andbe measured by rotation of the rotor 60 within the channel 56 from inletto outlet as divided by the rotary gate 68. The rotor 60 has a pluralityof blades 58 interacting with the rotary gate 68 in timed relationthrough gears 112 and l 14, respectively.

The housing 24 has a stationary liner 38 fixed thereto, and a stationarycrescent-shaped member 46a having an end flange 48a fixed to the liner38 by fastenings 50. The stationary body 42 is defined by the housing 24and liner 38 and other stationary parts affixed thereto. The rotor 60has an end ring 96 affixed to the end of the blades 58. The end ring 96has an inner circular trackway 100a. A further description of thestructure and operation of meter 22a may be had by reference to that setforth hereinbefore under the meter 22.

The bearing assembly 220 as best seen in FIGS. 9 and 10, includes asupport means 222 having an axially adjustable support ring 224 andsupport ring 226 axially fixed and formed integrally with the end flange48a, a split raceway or inner bearing race 160a, upon which isrotatively mounted a rotary means 162a having a cage means 164a and aplurality of circumferentially spaced cylindrical rollers 102a, a pairof axially spaced garter springs 168a which act to radially collapse theraceway 160a, and positioning means 228 in the form of screws 230 andnuts 232, which act to assemble and adjust the bearing assembly 220. Thebearing assembly 220 is mounted on a circular section 182a of the member46a formed inwardly of the end flange 48a thereof, and will rotativelysupport and center one end of the rotor 60.

The rotary means 162a has a plurality of cylindrical rollers 102asupported within the inner trackway 170a of the split raceway 160a. Therollers 102a in turn support and concentrically position the rotor 60 bycontact on the outer circular trackway 100a. The outer trackway 100a isa flat cylindrical surface machined on the inside diameter of the endring 96 of the rotor 60.

The cage means 164a illustrated in FIGS. 10 and 11 include a pluralityof links 234 having a slight longitudinal curvature and a hollow centralportion 236 from one side of which extends a pair of arms 238 of thesame width as the central portion, and the other side of which extends apair of arms 240, each formed inwardly of the edge so as to be ofsmaller width than the arms 238, so as to fit within the arms 238 of theadjacent link 234. A pin or axle 212a journals the rollers 102a andinterconnects adjacent links 234 at the overlapping arms 238 and 240thereof. The roller 102a has integral spacers 214a formed on either sidethereof adjacent the arms 240, so as to prevent binding or interferencewith the rotary motion of the rollers 102a. The interconnection betweenthe links 234, rollers 102a and axles 212a, is sufficiently loose topermit adjustment of the diameter of the raceway 160a.

The raceway 160a has two chamfered surfaces 178a machined at each end ofthe inside diameter thereof, which chamfered surfaces define a wedgemeans 176a. The raceway 160a is supported via contact of the chamferedsurfaces 178a with a curved shoulder 188a and 190a, which shoulders aremachined on the support ring 226 and 224, respectively. The curvedshoulders 188a and 190a define a wedge means 198a. It will be understoodthat the specific shapes and form of the wedge means of either of theembodiments, as for example, wedge means 176a and 198a could be changed,or reversed, or modified to another configuration, so long as the resultproduced the desired coaction and wedging action between the supportmeans and the raceway to adjust the diameter of the latter.

The raceway a is obliquely or transversely split as at a, so that theraceway 160a is free to expand or contract in diameter as desired. Thesplit 180a is formed at an angle to the center line of the raceway 160ato permit smooth operation of the load-carrying rollers 102a over saidsplit because a portion of the roller line of contact is alwayssupported by the inner trackway 170a on either side of the said split.

The two garter springs 168a are disposed in annular grooves 172a formedon the outer diameter of the raceway 160a on either side of the innertrackway 170a. The garter springs 168a tend to collapse the diameter ofthe raceway 160a, thus, securely to clamp the chamfered surfaces 178aupon the round shoulders 188a and a respectively of the rings 226 and224. The axes of the circular section 182a and the ring 226a, eachformed integrally on the member 46a, are concident to the axis ofrotation 82. Also, by manufacture, the round support shoulder 188a ofthe support ring 226 is concentric to and circular in reference to theaxis of rotation 82. Accordingly, raceway 160a will also assume asimilar circular and concentric relationship with the axis of rotation;82 through the engagement between the round annular shoulder 188a andthe wedge surface 1780.

The support ring 224 is axially adjustable and free to float on thecircular section 182a, and is positioned thereon by the three adjustingscrews 230 threadedly engaged in the tapped holes 242, as shown in FIGS.9 and 10. The support ring 224 is centered in reference to the raceway160a by contact of the round shoulder 190a with the chamfered surface178a of the raceway 160a. Since the round shoulder 190a is machinedperfectly round, it will likewise maintain the split raceway 160a in around condition due to the clamping action of the garter spring 168a.

The bearing assembly 220 as illustrated in FIG. 13, initially is mountedin the meter 22a by passing the screws 230 through holes 244 formed inthe member 46a at the end thereof adjacent the end flange 48a andsupport ring 226. The screws are threadedly received in the tapped holes242 of the support ring 224, so as to position the raceway 160a androtary means 162a upon the support means 222. The end of the screw 230extends beyond the end flange 48a and is threaded. A washer 246 isdisposed on the free end of screw 230 which then threadedly receives thenut 232 thereon. In the initial assembly position, the bearing assembly220 has the raceway 160a in unadjusted position and for purposes ofFIGS. 13 and 17, it is assumed that the rotor 60 is in non-concentricposition with respect to the axis of rotation 82. FIGS. 13 through 18illustrate a diagrammatic representation which assumes that theadjustment necessary on the diameter of the raceway 160a requires radialexpansion thereof, but of course, the same principles of the inventionwould apply had a radial reduction in said diameter been required tocenter the rotor 60. FIG. 13 indicates a clearance space 248 existsbetween the roller 102a and the outer trackway 100a so as to requireadjustment of the diameter of the raceway 160a of the bearing assembly220. Of course, whether the clearance space 248 existed or not, if therotor is in non-concentric position represented by FIG. 17, the bearingassembly 220 would require adjustment so as to center the same and therotor 60 with respect to the axis of rotation 82 so as to place therotary and stationary parts in concentric relationship to the axis ofrotation 82.

Accordingly, adjustment of the diameter of the raceway 160;: is made byturning the lock nuts 232 on the adjusting screws 230. When the nuts 230are turned so that the horizontal gap 2190 between the support rings224i and 226 is reduced, the diameter of the raceway 160a is increaseddue to the wedge action of the round support shoulders 188a and 190a onthe respective chamfered surfaces 178a of the raceway 160a. In FIG. 15,the contact point of the chamfered surface 178a of the raceway 160a withthe shoulder 190a is indicated at the point designated by the referencecharacter A. The contact point A of the chamfered surface 178aillustrated in FIG. corresponds to its respective position shown in FIG.13. In such an unadjusted position, the rotor 60 is depicted in FIG. 17as being in non-concentric position.

After adjustment of the diameter of the raceway 160a by expanding thesame as depicted in FIG. 14, the point A located on the chamferedsurface 178a is no longer in contact with the rounded shoulder 190a, butrather, the raceway 160a has been forced to expand because of thewedging action of the axially spaced rounded shoulders 188a and 1900 tobring the rounded shoulder 190a into contact with a new point designatedgenerally by the reference character B. Though only the rounded shoulder190a has been shown in FIGS. '15 and 16, it will be understood that amirror image of FIGS. 15 and 16 would represent rounded shoulder 188a,so as to produce the same result. The bearing assembly 220 is shown inadjusted concentric position in FIGS. 14 and 18, whereby the diameter ofthe raceway 160a has been expanded as is indicated by the increasedclearance in the split 180a and the fact that the rollers 102 are incontact with the outer trackway 100a, so as to eliminate the clearance248 therebetween. Furthermore, as indicated in FIG. 18, the rotor 60 hasbeen forced into concentric position with respect to the axis ofrotation 82 by the adjustment of the bearing assembly 220.

Likewise, adjustment of the bearing assembly 220 can be had in certaininstances which require reduction of the diameter of the raceway 160a byturning the adjusting nuts 232 in a direction to increase the gap 219abetween the rings 224 and 226.

While a great range of materials may be utilized in the bearingassemblies 20 and 220, tests of said bearing assemblies have indicatedthat the use of dissimilar materials for the rollers 102 and 102arespectively, and the raceway 160 and 160a respectively, said bearingassembly can be constructed which will not require lubrication. In oneparticular application, it has been found -that plastic rollers and ahard anodized aluminum raceway are satisfactory for operation atmoderate speeds of 1,400 rpm. and the fairly light loads encountered inrotary meter design.

It will be understood that various changes in the details, materials,arrangements of parts and operating conditions which have been hereindescribed and illustrated in order to explain the nature of theinvention may be made by those skilled in the art within the prin'ciples and scope of the invention.

Having thus set forth the nature of the invention, what is claimedherein is:

I. A bearing for a machine having a stationary housing with a fixed axisabout which axis a rotating member rotates comprising:

a. a support means including an axially movable ring means,

b. a split raceway mounted upon the support means to be radiallyshiftable responsive to axial movement of the ring means,

0. rotary means engaging the raceway and adapted to be rotatedthereabout, and

d. connecting means adjustably affixed to the stationary housing toengage the support means to cause the raceway radially to shift andengage the rotating member.

2. The combination claimed in claim 1 wherein:

a. the raceway has an oblique split with respect to the axis.

3. The combination claimed in claim 1 wherein:

a. wedge means is formed on the support means,

b. wedge means is formed on the raceway to coact with the wedge means ofa support means, and

c. annular spring means mounted upon the raceway to collapse the racewayand urge the wedge means of the raceway into contact with the wedgemeans of the support means.

. The combination claimed in claim 3 wherein:

a. the stationary housing extends within the rotating member,

b. the support means includes a pair of spaced rings, one being axiallymovable with respect to the other, and

c. the spring means includes a pair of annular springs mounted upon theraceway in superposition to each of the wedge means of the rings toprovide continuous contact therebetween.

5. The combination claimed in claim 4 wherein:

a. the wedge means of the raceway define a chamfered surface,

b. the wedge means of the rings define an arcuate shoulder, and

c. the connecting means includes three axially disposed screw means, theadjustment of which will shift the annular point contact between thechamfered surface and the arcuate shoulder to force the raceway toexpand or to permit the raceway to contract.

6. A machine comprising:

. a stationary means having an axis of rotation,

a rotating member adapted to be rotated with respect to the stationarymeans about the axis of rotation,

c. the stationary means including a pair of support members, at leastone of which is axially shiftable,

d. annular wedge means formed on at least one of the support members,

e. the wedge means has an axis coincident to the axis of rotation,

f. a raceway means, having an adjustable diameter and at least oneannular wedge surface means, is mounted on the support means,

g. the wedge surface means of the raceway means to coact with the wedgemeans of the support member,

. a rotary means is rotatively disposed upon the raceway means, and

. adjustable positioning means connected to the support means to axiallyshift the same and cause engagement between the wedge surface means andthe wedge means radially to shift the raceway means to force the rotarymeans against the rotating member.

. The combination claimed in claim 6 wherein:

a. the raceway means has a transverse axial'opening thereacrosspermitting expansion or contraction of the diameter thereof, and

. a spring means carried by the raceway means to urge the raceway toassume a contracted diameter.

. The combination claimed in claim 7 wherein:

. the spring means disposed above the wedge surface means to urge theraceway means against the wedge means of the support member.

. The combination claimed in claim 8 wherein:

. the wedge means of the support member is formed circularly, and thespring means is annular and urges the raceway means into annular pointcontact with the wedge means, whereby the raceway assumes a circularshape corresponding to that of the wedge means.

10. The combination claimed in claim 9 wherein:

a. the wedge means has an axis coincident to the axis of the stationarymeans, and

b. the positioning means equidistantly spaced about the axis to urgeaxial movement of the support member in a plane perpendicular to theaxis to force the axis of the raceway to correspond to the axis of thewedge means in coincident position to the axis of the stationary means.

11. An adjustable diameter bearing to be mounted about an axis ofrotation comprising:

a. a pair of support members,

b. a split raceway mounted upon the support members,

c. wedge means formed on the support members,

d. wedge means formed on the raceway,

e. spring means disposed about the raceway to urge the wedge means ofthe raceway into engagement with the wedge means of the support members,

f. positioning means interconnecting the support members in an axiallyadjustable position with respect to one another, whereby axiallypositioning of the support means results in radially shifting theraceway, and

g. rotary means rotatively mounted about the raceway. 1

12. The combination claimed in claim 11 wherein:

a. the support members are axially spaced from each other with the wedgemeans thereof facing each other,

b. one of the support members axially moveable towards or away from theother support member, and

c. the wedge means of the raceway formed on either side thereof tocontact the wedge means of the support members.

13. The combination claimed in claim 12 wherein:

a. the wedge means of the support members are formed to contact thewedge means of the raceway at radial points equally spaced from the axisof rotation to center the raceway with respect to the axis of rotation.

14. The combination claimed in claim 13 wherein:

a. the wedge means of the support members are formed annularly with theaxes thereof coincident to the axis of rotation, and

b. the positioning means to clamp the raceway between the supportmembers to force the raceway into a concentric position with respect tothe axis of rotation.

15. The combination claimed in claim 11 wherein:

a. the rotary means includes an annular cage having a plurality ofrollers rotatively mounted therein and circumferentially spaced fromeach other.

16. The combination claimed in claim 15 wherein:

a. the annular cage includes a plurality of interconnected links, and

b. the links loosely connected to each other to permit expansion andcontraction of the raceway.

17. The combination claimed in claim 16 wherein:

a. an axle interconnecting successive links to each other and to one ofthe rollers to form an endless cage means.

18. The combination claimed in claim 17 wherein:

a. the axles, the links and the rollers are formed in equal numbers intothe cage means.

19. A bearing for a machine having a stationary member with a fixed axisabout which axis a rotating member rotates comprising: i

a. a support means including an axially movable circular ring means,

b. a split raceway mounted upon the support means to be radiallyshiftable responsive to axial movement of the ring means,

0. rotary means engaging the raceway and adapted to be rotatedthereabout, and

d. positioning means adjustably affixed to the stationary housing toengage the support means to effect axial centering of the ring means andthe raceway with respect to the axis of rotation, and to cause theraceway radially to shift and to force the rotary means concentricallyto engage the rotating member.

20. The combination claimed in claim 19 wherein:

a. the support ring is split,

b. spring means disposed on the raceway to collapse the same and thesplit support ring to bring the ring into centered contact upon thestation member.

21. The combination claimed in claim 19 wherein:

a. the support means include a pair of support members, one of which isaxially stationary and one of which is axially movable, and

b. one of the support members is supported by the positioning means innonsupported radial contact with the stationary member.

22. The combination claimed in claim 19 wherein:

a. wedge means formed on the support means,

b. the wedge means to engage the raceway and responsive to movement ofthe positioning means to expand or contract the diameter of the raceway.

23. The combination claimed in claim 19 wherein:

a. spring means mounted upon the raceway to collapse the same to bringthe raceway into annular contact with the support ring.

24. The combination claimed in claim 23 wherein:

a. the positioning means to urge the support ring and the raceway to bein axial contact with each other,

b. wedge means formed on the support ring and the raceway to interacttherebetween,

raceway.

1. A bearing for a machine having a stationary housing with a fixed axisabout which axis a rotating member rotates comprising: a. a supportmeans including an axially movable ring means, b. a split racewaymounted upon the support means to be radially shiftable responsive toaxial movement of the ring means, c. rotary means engaging the racewayand adapted to be rotated thereabout, and d. connecting means adjustablyaffixed to the stationary housing to engage the support means to causethe raceway radially to shift and engage the rotating member.
 2. Thecombination claimed in claim 1 wherein: a. the raceway has an obliquesplit with respect to the axis.
 3. The combination claimed in claim 1wherein: a. wedge means is formed on the support means, b. wedge meansis formed on the raceway to coact with the wedge means of a supportmeans, and c. annular spring means mounted upon the raceway to collapsethe raceway and urge the wedge means of the raceway into contact withthe wedge means of the support means.
 4. The combination claimed inclaim 3 wherein: a. the stationary housing extends within the rotatingmember, b. the support means includes a pair of spaced rings, one beingaxially movable with respect to the other, and c. the spring meansincludes a pair of annular springs mounted upon the raceway insuperposition to each of the wedge means of the rings to providecontinuous contact therebetween.
 5. The combination claimed in claim 4wherein: a. the wedge means of the raceway define a chamfered surface,b. the wedge means of the rings define an arcuate shoulder, and c. theconnecting means includes three axially disposed screw means, theadjustment of which will shift the annular point contact between thechamfered surface and the arcuate shoulder to force the raceway toexpand or to permit the raceway to contract.
 6. A machine comprising: a.a stationary means having an axis of rotation, b. a rotating memberadapted to be rotated with respect to the stationary means about theaxis of rotation, c. the stationary means including a pair of supportmembers, at least one of which is axially shiftable, d. annular wedgemeans formed on at least one of the support members, e. the wedge meanshas an axis coincident to the axis of rotation, f. a raceway means,having an adjustable diameter and at least one annular wedge surfacemeans, is mounted on the support means, g. the wedge surface means ofthe raceway means to coact with the wedge means of the support member,h. a rotary means is rotatively disposed upon the raceway means, and i.adjustable positioning means connected to the support means to axiallyshift the same and cause engagement between the wedge surface means andthe wedge means radially to shift the raceway means to force the rotarymeans against the rotating member.
 7. The combination claimed in claim 6wherein: a. the raceway means has a transverse axial opening thereacrosspermitting expansion or contraction of the diameter thereof, and b. aspring means carried by the raceway means to urge the raceway to assumea contracted diameter.
 8. The combination claimed in claim 7 wherein: a.the spring means disposed above the wedge surface means to urge theraceway means against the wedge means of the support member.
 9. Thecombination claimed in claim 8 wherein: a. the wedge means of thesupport member is formed circularly, and b. the spring means is annularand urges the raceway means into annular point contact with the wedgemeans, whereby the raceway assumes a circular shape corresponding tothat of the wedge means.
 10. The combination claimed in claim 9 wherein:a. the wedge means has an axis coincident to the axis of the stationarymeans, and b. the positioning means equidistantly spaced about the axisto urge axial movement of the support member in a plane perpendicular tothe axis to force the axis of the raceway to correspond to the axis ofthe wedge means in coincident position to the axis of the stationarymeans.
 11. An adjustable diameter bearing to be mounted about an axis ofrotation comprising: a. a pair of support members, b. a split racewaymounted upon the support members, c. wedge means formed on the supportmembers, d. wedge means formed on the raceway, e. spring means disposedabout the raceway to urge the wedge means of the raceway into engagementwith the wedge means of the support members, f. positioning meansinterconnecting the support members in an axially adjustable positionwith respect to one another, whereby axially positioning of the supportmeans results in radially shifting the raceway, and g. rotary meansrotatively mounted about the raceway.
 12. The combination claimed inclaim 11 wherein: a. the support members are axially spaced from eachother with the wedge means thereof facing each other, b. one of thesupport members axially moveable towards or away from the other supportmember, and c. the wedge means of the raceway formed on either sidethereof to contact the wedge means of the support members.
 13. Thecombination claimed in claim 12 wherein: a. the wedge means of thesupport members are formed to contact the wedge means of the raceway atradial points equally spaced from the axis of rotation to center theraceway with respect to the axis of rotation.
 14. The combinationclaimed in claim 13 wherein: a. the wedge means of the support membersare formed annularly with the axes thereof coincident to the axis ofrotation, and b. the positioning means to clamp the raceway between thesupport members to force the raceway into a concentric position withrespect to the axis of rotation.
 15. The combination claimed in claim 11wherein: a. the rotary means includes an annular cage having a pluralityof rollers rotatively mounted therein and circumferentially spaced fromeach other.
 16. The combination claimed in claim 15 wherein: a. theannular cage includes a plurality of interconnected links, and b. thelinks loosely connected to each other to permit expansion andcontraction of the raceway.
 17. The combination claimed in claim 16wherein: a. an axle interconnecting successive links to each other andto one of the rollers to form an endless cage means.
 18. The combinationclaimed in claim 17 wherein: a. the axles, the links and the rollers areformed in equal numbers into the cage means.
 19. A bearing for a machinehaving a stationary member with a fixed axis about which axis a rotatingmember rotates comprising: a. a support means including an axiallymovable circular ring means, b. a split raceway mounted upon the supportmeans to be radially shiftable responsive to axial movement of the ringmeans, c. rotary means engaging the raceway and adapted to be rotatedthereabout, and d. positioning means adjustably affixed to thestationary housing to engage the support means to effect axial centeringof the ring means and the raceway with respect to the axis of rotation,and to cause the raceway radially to shift and to force the rotary meansconcentrically to engage the rotating member.
 20. The combinationclaimed in claim 19 wherein: a. the support ring is split, b. springmeans disposed on the raceway to collapse the same and the split supportring to bring the ring into centered contact upon the station member.21. The combination claimed in claim 19 wherein: a. the support meansinclude a pair of support members, one of which is axially stationaryand one of which is axially movable, and B. one of the support membersis supported by the positioning means in nonsupported radial contactwith the stationary member.
 22. The combination claimed in claim 19wherein: a. wedge means formed on the support means, b. the wedge meansto engage the raceway and responsive to movement of the positioningmeans to expand or contract the diameter of the raceway.
 23. Thecombination claimed in claim 19 wherein: a. spring means mounted uponthe raceway to collapse the same to bring the raceway into annularcontact with the support ring.
 24. The combination claimed in claim 23wherein: a. the positioning means to urge the support ring and theraceway to be in axial contact with each other, b. wedge means formed onthe support ring and the raceway to interact therebetween, c. the wedgemeans responsive to axial shifting of the support ring to cause radialshifting of the raceway.